Stacked Disk Check Valve

ABSTRACT

Fluid apparatus and related methods are disclosed. An example fluid apparatus includes a valve body defining a fluid flow passageway and a plurality of valve seats. A flow control member is positioned in the fluid flow passageway of the valve body. The flow control member having a plurality of disks. A respective one of the disks moves relative to a respective one of the valve seats to control fluid flow through the valve body. The flow control member is adjustable relative to a longitudinal axis of the valve body to provide a preload to the disks. Each of the disks has a cracking pressure corresponding to the preload.

GOVERNMENT CONTRACT

This invention was made with government support under HR0011-14-9-0005.The government has certain rights in the invention.

FIELD OF THE DISCLOSURE

This patent relates generally to fluid devices and, more particularly,to valve apparatus and related methods.

BACKGROUND

Fluid systems (e.g., fuel systems, propulsion systems, hydraulicsystems, etc.) often employ fluid devices (e.g., check valves) toprevent reverse fluid flow through the system. For example, a spaceshuttle propulsion system may employ check valves to prevent reversefluid flow to a main engine of a space shuttle. Check valves typicallyinclude a ball valve that moves relative to a valve seat to controlfluid flow through the check valve. In some examples, a spring is oftenemployed to bias the ball valve into sealing engagement with the valveseat. In some examples, the spring may be adjustable to vary a preloadto adjust or set a desired cracking pressure of the valve (i.e., apressure at which the ball valve moves to an open position away from thevalve seat to allow fluid through the valve). However, in someinstances, the spring may wear or fracture due to cyclic fatigue orcryogenic shock. As a result, the valve ay open at a pressure less thanthe desired cracking pressure provided by the initial preload or,alternatively, there may be reverse flow (fluid flow from the outlettoward the inlet). In sonic instances, a change in pressure across anorifice of the fluid valve may produce vibration having a frequencysimilar or the same as a resonant frequency of the spring, which causeschattering. In some instances, for example during high vibrationalapplications, the ball valve may dislodge (e.g., from the impetus of thespring) and fall from the valve seat.

Some known check valves employ a spring-biased swing flapper. However,in some applications, fluid flow may cause cyclic wear on the springand/or flapper due to spring-flapper oscillations. In some examples,springless or spring-free check valves employ a flap that moves ordeflects relative to a valve seat to control fluid flow. However, acracking pressure of springless check valves may not be adjustable. Insome instances, the flaps could chatter and/or become damaged duringhigh vibrational applications. Thus, the flap may be subject to chatterduring certain flow conditions that prevent the flap from providing adesired shut-off or seal.

SUMMARY

An example fluid apparatus disclosed herein includes a valve bodydefining a fluid flow passageway and a plurality of valve seats. A flowcontrol member is positioned in the fluid flow passageway of the valvebody. The flow control member having a plurality of disks. A respectiveone of the disks moves relative to a respective one of the valve seatsto control fluid flow through the valve body. The flow control member isadjustable relative to a longitudinal axis of the valve body to providea preload to the disks. Each of the disks has a cracking pressurecorresponding to the preload.

Another example apparatus includes a valve body defining a valve seatpositioned in a fluid flow passageway between an inlet and an outlet anda threaded inner wall and a flow control member positionable in thefluid flow passageway. The flow control member including: a body; a diskcoupled to the body, where the disk is to seal against the valve seat toprevent fluid flow through the fluid flow passageway when a pressure atan inlet of the valve body is less than a cracking pressure of the diskand the disk is to move away from the valve seat to allow fluid flowthrough the fluid flow passageway when the pressure at the inlet of thehousing is greater than or equal to the cracking pressure; and a headhaving threaded portion to engage the threaded inner wall of the valvebody to couple the flow control member to the valve body, where the headis adjustable relative to a longitudinal axis of the valve body toprovide a preload to the disk corresponding to the cracking pressure.

An example method disclosed herein includes positioning a flow controlmember in a first housing of a fluid valve, where the first housing hasa plurality of valve seats and the flow control member has a pluralityof disks. The valve seats and the disks are spaced along a longitudinalaxis of the first housing such that a respective one of the disks is toengage a respective one of the valve seats when the flow control memberis positioned in the first housing. The method includes adjusting aposition of the flow control member relative to the longitudinal axis tovary a preload of the plurality of disks.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a perspective view of an example fluid apparatus constructedin accordance with the teachings disclosed herein.

FIG. 2 is a cross-sectional view of the fluid apparatus of FIG. 1.

FIG. 3 is a perspective view of an example first housing of the examplefluid apparatus of FIGS. 1-2.

FIG. 4 is a perspective, cross-sectional view of the example firsthousing of FIG. 3.

FIG. 5 is a perspective view of an example second housing of the examplefluid apparatus of FIGS. 1-2.

FIG. 6 is a perspective, cross-sectional view of the example secondhousing of FIG. 5.

FIG. 7A is a perspective view of an example flow control member of theexample fluid apparatus of FIGS. 1 and 2.

FIG. 7B is another perspective view of an example flow control member ofthe example fluid apparatus of FIGS. 1, 2, and 7B.

FIG. 8A is an enlarged, cross-sectional view of a portion of the exampleflow control member of FIGS. 1, 2, 7A and 7B.

FIGS. 8B and 8C are partial, perspective views of the example flowcontrol member of FIGS. 1, 2, 7A and 7B.

FIG. 8D is a cross-sectional view of a rib of the example flow controlmember of FIGS. 1, 2, 7A, 7B and 8A-8C.

FIG. 8E is a side view of the example flow control member of FIGS, 1, 2,7A, 7B, and 8A-8D.

FIG. 9 is another perspective, cross-sectional view of an example fluidapparatus of FIGS. 1-6, 7A-7B, and 8A-8E.

FIG. 10 is a cross-sectional view of the example fluid apparatus ofFIGS. 1-6, 7A-7B, 8A-8E and 9 shown in a closed position.

FIG. 11 is a cross-sectional view of the example fluid apparatus ofFIGS. 1-6, 7A-7B, 8A-8E, 9 and 10 shown in an open position.

FIG. 12 is a cross-sectional view of another example fluid apparatusdisclosed herein.

FIG. 13 is a cross-sectional view of another example fluid apparatusdisclosed herein.

FIG. 14 is a cross-sectional view of another example fluid controlapparatus disclosed herein.

FIG. 15 is a perspective, cross-sectional view of another example fluidapparatus disclosed herein.

FIG. 16A is a perspective, cross-sectional view of another example fluidapparatus disclosed herein.

FIG. 16B is a perspective view of another example flow control memberdisclosed herein that may implement an example fluid apparatus disclosedherein.

FIG. 16C illustrates another example flow control member disclosedherein that may implement an example fluid apparatus disclosed herein.

FIG. 16D illustrates another example flow control member disclosedherein that may implement an example fluid apparatus disclosed herein

FIG. 17 illustrates an example method to manufacture, fabricate orassemble an example fluid apparatus disclosed herein.

FIG. 17 illustrates an example method to manufacture, fabricate orassemble an example fluid apparatus disclosed herein.

FIG. 18 illustrates an example method to assemble an example fluidapparatus disclosed herein.

FIG. 19 illustrates an example method of operation an example fluidapparatus disclosed herein.

Wherever possible, the same reference numbers will be used throughoutthe drawing(s) and accompanying written description to refer to the sameor like parts. As used in this description, stating that any part (e.g.,a layer, film, area, or plate) is in any way positioned on (e.g.,positioned on, located on, disposed on, or formed on, etc.) anotherpart, means that the referenced part is either in contact with the otherpart, or that the referenced part is above the other part with one ormore intermediate part(s) located there between. Stating that any partis in direct contact with another part means that there is nointermediate part between the two parts. As used herein, substantiallyand approximately mean within about 10% different than the number atissue. For example, substantially perpendicular means 90 degrees plus orminus 10%. For example, approximately 90 degrees means 90 degrees plusor minus 10% (e.g., between about 81 degrees and 99 degrees). In someexamples, substantially parallel means 0 degrees plus or minus 10degrees.

DETAILED DESCRIPTION

The example fluid apparatus disclosed herein may be employed withcontrol systems to control the flow of fluids. In some examples, theexample fluid apparatus disclosed herein may be configured as checkvalves that prevent reverse fluid flow through a fluid control system(e.g., a fuel system, a hydraulic system, etc.). The example fluidapparatus disclosed herein may be employed aerospace applications orsystems (e.g., a spacecraft, an aircraft, a space station system),automotive applications or systems, industrial systems, applicationshaving cryogenic conditions, and/or any other application or systemrequiring fluid flow control (e.g., prevention of reverse fluid flow).For example, the example fluid apparatus disclosed herein may beemployed in propulsion systems (e.g., a rocket or spacecraft propulsionsystem), fuel systems (e.g., an automotive fuel system), hydraulicsystems, and/or any other process or system requiring fluid flow control(e.g., prevention of reverse fluid flow).

The example fluid apparatus disclosed herein reduce weight and/ormanufacturing costs compared to conventional check valves (e.g., a ballcheck valve, a swing valve, a diaphragm check valve, etc.).Additionally, the example fluid apparatus disclosed herein may provideimproved sealing compared to conventional fluid valves (e.g., checkvalves). In some examples, the fluid apparatus disclosed herein mayprovide redundant sealing. For example, the example fluid apparatusdisclosed herein may employ multiple flow control members (e.g.,multiple stacked disks) and/or valve seats to provide redundant sealing.In sonic examples, the fluid apparatus disclosed herein may include onlyone disk and/or only one valve seat.

In some examples, the fluid apparatus disclosed herein enable preload orcracking pressure tuning or adjustment without use of a spring. Forexample, a cracking pressure or pressure required to open the examplefluid apparatus may be adjusted or varied to a desired pressure withoutrequiring use of a biasing element or spring. For example, to adjust acracking pressure or preload of the valve, an example flow controlmember disclosed herein includes a threaded portion to engage a threadedwall of a housing to enable (e.g., linear) adjustment of the flowcontrol member along the longitudinal axis. In some examples, apassageway and/or a rib of the example fluid flow control membersdisclosed herein may include a profile (e.g., an airfoil profile and/ora tapered profile) to promote laminar flow characteristics and/orprevent turbulent fluid flow characteristics when fluid flows throughthe fluid apparatus. In some examples, the fluid apparatus disclosedherein may be conducive to cryogenic environments or conditions and/orare resistant to vibration loading. In some examples, the fluidapparatus disclosed herein may be composed of any material(s) or alloyssuch as, for example, Inconel, steel, aluminum, plastic, PTFE, Teflon,and/or any other material(s). In some examples, the material of the flowcontrol member may provide different cracking pressures based on atemperature of a process fluid and/or a temperature of an environment ofthe valve. In some examples, the example fluid apparatus disclosedherein may be manufactured using an additive manufacturing process(e.g., a direct metal laser sintering additive manufacturing processinjection molding, machining and/or any other manufacturing process(es).In some examples, the fluid apparatus disclosed herein employ aplurality of disks. In some examples, the disks are spaced along alongitudinal axis of a flow control member. In some examples, the disksare concentric.

FIG. 1 illustrates an example fluid apparatus 100 in accordance with theteachings of this disclosure. The example fluid apparatus 100 of theillustrated example is a check valve that enables one-way fluid flowfrom an upstream source 102 of a system 104 toward a downstream source106 of the system 104. In addition, the example fluid apparatus 100 ofthe illustrated example prevents fluid flow from the downstream source106 toward the upstream source 102. In some examples, the system 104 maybe a portion of a space shuttle main propulsion system and/or anotherre-entry vehicle. For example, the upstream source 102, the fluidapparatus 100 and the downstream source 106 may be part of a bleedreturn line of a spacecraft propulsion system.

FIG. 2 is a cross-sectional, perspective view of the example fluidapparatus 100 of FIG. 1. The example fluid apparatus of the illustratedexample includes a housing 202 having a first housing portion 204 (e.g.,a bonnet) coupled to a second housing portion 206 (e.g., a valve body).The first housing portion 204 and the second housing portion 206 of theillustrated example (e.g., when coupled together via, for example,fasteners 207) define a fluid flow passageway 208 (e.g., an axial fluidflow path) between an inlet 210 and an outlet 212. The inlet 210 of theillustrated example is coaxially aligned with the outlet 212.Additionally, the inlet 210 and the outlet 212 of the illustratedexample are coaxially aligned relative to a longitudinal axis 214 of thefluid apparatus 100 and/or the fluid flow passageway 208. In someexamples, the inlet 210 may not be coaxially aligned with the outlet 212and/or the longitudinal axis 214.

To control fluid flow between the inlet 210 and the outlet 212 theexample fluid apparatus 100 includes a flow control member 216 (e.g., apoppet) positioned in the fluid flow passageway 208. In the illustratedexample, the flow control member 216 includes radial flanges or disks218 (e.g., multiple stacked disks). In particular, the disks 218 of theexample flow control member 216 are spaced along a length of the flowcontrol member 216 (e.g., concentrically aligned). The disks 218 of theexample flow control member 216 move relative to (e.g., engage anddisengage) respective valve seats 220 of the fluid apparatus 100 tocontrol (e.g., prevent or allow) fluid flow through the fluid flowpassageway 208. As described in greater detail below, the example disks218 provide redundant sealing. In addition, the example flow controlmember 216 of the illustrated example provides a preload to the disks218 without use of a biasing element such as, for example, a spring.Seals 222 and 224 between the first housing portion 204 and the secondhousing portion 206 prevent fluid flow leakage external of the housing202 when fluid flows between the inlet 210 and the outlet 212.

FIG. 3 is a perspective view of the first housing portion 204 of FIGS. 1and 2. The first housing portion 204 of the illustrated example includesa body 302 having a first end 304 and a second end 306 opposite thefirst end 304. The body 302 of the illustrated example includes a flange308 adjacent the first end 304 and the outlet 212 adjacent the secondend 306. The body 302 of the illustrated example includes a cylindricalportion 310 extending from the flange 308 and a tapered portion 312extending between the cylindrical portion 310 and the outlet 212. Tocouple the downstream source 106 (FIG. 1) to the fluid apparatus 100,the body 302 of the illustrated example includes a fitting 314. In theillustrated example, the fitting 314 is integrally formed with the body302 and extends from the tapered portion 312. The fitting 314 of theillustrated example is a threaded male fitting. In some examples, thefitting 314 may be a threaded female fitting, a barb, a quick disconnectfitting, a swage lock, a flange, and/or any other fitting(s). The flange308 of the illustrated example includes holes 316 radially spacedrelative to a longitudinal axis 318 of the body 302. To reduce mass,material cost, manufacturing time, etc., a peripheral edge 320 of theflange 308 of the illustrated example includes a sinusoidal shape orprofile 322 and a chamfer 324 (e.g., a 45 degree angle). In someexamples, the peripheral edge 320 of the flange 308 may include acircular shape or any other shape and/or may not include the chamfer324.

FIG. 4 illustrates a cross-sectional, perspective view of the firsthousing portion 204 of FIG. 3. The body 302 of the first housing portion204 has a cavity 402 to form a portion of the fluid flow passageway 208of the fluid apparatus 100. In the illustrated example, at least aportion of an inner surface 404 of the cylindrical portion 310 includesthreads 406. As described in greater detail below, the threads 406 ofthe body 302 couple the flow control member 216 to the fluid apparatus100.

FIG. 5 is a perspective view of the example second housing portion 206of FIGS. 1 and 2. The second housing portion 206 includes a body 502(e.g., a cylindrical body) and a flange 504. The flange 504 is adjacenta first end 506 of the body 502 (e.g., a cylindrical body) and a secondend 508 of the body 502 opposite the first end 506 defines the inlet Tocouple the fluid apparatus 100 to the upstream source 102 of FIG. 1, thesecond housing portion 206 of the illustrated example includes a fitting510 adjacent the inlet 210. The fitting 510 of the illustrated exampleis integrally formed with the body 502 and is a threaded male fitting.In some examples, the fitting 510 may be a threaded female fitting, abarb, a quick disconnect fitting, a swage lock, a flange, and/or anyother fitting(s). The flange 504 of the illustrated example includesholes 512. To reduce mass, material cost, manufacturing time, etc., aperipheral edge 514 of the flange 504 of the illustrated exampleincludes a sinusoidal shape or profile 516 and a chamfer 518 (e.g., a45-degree angle). In some examples, the peripheral edge 514 may includea circular shape and/or may not include the chamfer 518. To provide aseat for the seals 222 and 224 (e.g., O-rings), the body 502 of theillustrated example includes a first groove 520 (e.g., an annulargroove) and a second groove 522 (e.g., an annular groove). Each of thegrooves 520 and 522 of the illustrated example includes a U-shapedchannel. In some examples, the first groove 520 and/or the second groove522 may have V-shaped channel or profile.

FIG. 6 is a cross-sectional, perspective view of the example secondhousing portion 206 of FIG. 5. The body 502 has an opening 602 definingat least a portion of the fluid flow passageway 208. In addition, thebody 502 of the illustrated example defines the valve seats 220. Thevalve seats 220 of the illustrated example are integrally formed withthe body 502. In some examples, the valve seats 220 may be separateparts that can be coupled (e.g., via threads, press-fit, etc.) to thebody 502. In the illustrated example, the body 502 includes three valveseats 604, 606, 608 that define respective orifices of the fluid flowpassageway 208.

To provide the valve seats 220, the body 502 of the illustrated exampleincludes a plurality of stepped surfaces 610. A first stepped surface610 a has a first dimension (e.g., a first radius R₁) relative to alongitudinal axis 611 of the body 502, a second stepped surface 610 bhas a second dimension (e.g., a second radius R₂) relative to thelongitudinal axis 611, and a third surface 610 c has a third dimension(e.g., a third radius R₃) relative to the longitudinal axis 611. In theillustrated example, the first dimension is smaller than the seconddimension and the third dimension, and the second dimension is smallerthan the third dimension. However, in some examples, the first dimensionmay be equal to the second dimension and/or the third dimension. In theillustrated example, the first stepped surface 610 a or valve seat 604is spaced from the second stepped surface 610 b or valve seat 606 (e.g.,in a vertical direction in the orientation of FIG. 6) by a distance L₁and the second stepped surface 610 b or valve seat 606 is spaced fromthe third stepped surface 610 c or valve seat 608 by a distance L₂(e.g., a vertical distance in the orientation of FIG. 6). The thirdstepped surface 610 c is spaced from first end 506 (e.g., the flange504) by a third distance L₃. In some examples, the first distance L₁ isequal to the second distance L₂ and/or the third distance L₃. In someexamples, the first distance L₁ is different from the second distance L₂and/or the third distance L₃. In some examples, the second distance L₂is different than the third distance L₃.

To reduce stress concentration on the disks 218 and/or to improvesealing capability when the disks 218 engage and/or seal against thevalve seats 220, the stepped surfaces 610 may include a curved orarcuate profile 612 (e.g., fillets) and a curved or arcuate transition614 (e.g., a fillet) between a sealing surface 616 and an inner wall 618of the body 502. In some examples, the sealing surface 616 has a profileconfigured to engage (e.g., for matable engagement with) a profile ofthe disks 218. In some examples, the valve seats 220 may be polished(e.g., to less than 16 micro Ra (arithmetic mean roughness), betweenapproximately 5 micro Ra and 25 micro Ra (arithmetic mean roughness),etc.) to improve sealing. Additionally, the second housing portion 206(e.g., an inner surface of the second housing portion 206 and/or anouter surface of the second housing portion 206 (e.g., defining thestepped surfaces 610)) may include a radius of curvature or fillet(e.g., a 45 degree fillet) to reduce stress concentrations associatedwith cyclic loading or vibration.

FIGS. 7A and 7B are a perspective view of the example flow controlmember 216 of FIGS. 1 and 2. The example flow control member 216 of theillustrated example is a poppet having a body or pylon 702, a head 704and the plurality of disks 218. The pylon 702 of the illustrated examplesupports the disks 218. The pylon 702 of the illustrated example has atapered profile between a first end 706 of the pylon 702 adjacent thehead 704 and a second end 708 of the pylon 702 opposite the first end706. For example, a dimension (e.g., a radius) of the pylon 702 varies(e.g., continuously or incrementally decreases) between the first end706 and the second end 708. However, in some examples, the pylon 702 mayinclude a constant or non-varying diameter between the first end 706 andthe second end 708. The second end 708 of the pylon 702 of theillustrated example includes a cone-shaped end that forms a tip 702 a(e.g., a point). The second end 708 of the illustrated example has aprofile (e.g., a sloped or conical profile) that promotes laminar flowcharacteristics when a fluid flows across the second end 708 of the flowcontrol member 216.

The flow control member 216 of the illustrated example includes a firstdisk 710 to engage the first valve seat 604 (FIG. 6), a second disk 712to engage the second valve seat 606 (FIG. 6), and a third disk 714 toengage the third valve seat 608 (FIG. 6). The first disk 710 of theillustrated example is spaced from the second disk 712 by a firstdistance D₁ and the second disk 712 is spaced from the third disk 714 bya second distance D₂. In some examples, the first distance D₁ is equalto the second distance D₂. In some examples, the first distance D₁ isdifferent than the second distance D₂. The third disk 714 of theillustrated example is spaced from the head 704 a third distance D₃. Insome examples, the third distance D₃ is equal to the first distance D₁and the second distance D₂. In some examples, the third distance D₃ isdifferent than (e.g., greater than or less than) the first distance D₁and/or the second distance D₂. In some examples, the first distance L1is different than the first distance D1 and/or the second distance L2 isdifferent than the second distance D2. In this manner, the first disk710 may be at a different elevation or offset (e.g., above) relative tothe first valve seat 604, the second disk 712 may be at a differentelevation or offset (e.g., above) relative to the second valve seat 606,and/or the third disk 714 may be at a different elevation or offset(e.g., above) relative to the third valve seat 608.

Each of the disks 218 of the illustrated example has a central opening716 and a peripheral edge 718. The central opening 716 of each of thedisks 218 of the illustrated example receives the pylon 702. In theillustrated example, the central opening 716 defines an inner edge 716 athat is attached to the pylon 702. To reduce stress concentrationsassociated with cyclic loading fatigue (e.g., due to pressurization orvibration), a fillet is provided between the inner edge 716 a and thepylon 702. In the illustrated example, the peripheral edge 718 of theillustrated example includes a curve or arcuate shape to provide acurved lip 720 when the disks 218 are in a non-deflected position. Insome examples, the curved or arcuate profile of the peripheral edge 718provides or improves sealing when the disks 218 engage or seal againstthe respective valve seats 220. In some examples, the curved or arcuateprofile of the peripheral edge 718 promotes laminar flow characteristicsas fluid flows across or past the disks 218.

Each of the disks 218 of the illustrated example has a first face 722and a second face 724 opposite the first face 722 separated by athickness 726 of the disks 218. The first face 722 provides a sealingsurface to engage the valve seats 220. In some example, the disks 218and/or the first faces 722 may be polished (e.g., to less than 16 microRa (arithmetic mean roughness), between approximately 5 micro Ra and 25micro Ra, etc.) to improve sealing between the disks 218 and the valveseats 220. In some examples, the thickness 726 of the disks 218 mayaffect a cracking pressure of the fluid apparatus 100. For example, thethickness 726 of the disks 218 affects the cracking pressure of thefluid apparatus 100. For example, reducing the thickness 726 of thedisks 218 reduces cracking pressure and increasing the thickness 726 ofthe disks 218 increases cracking pressure. The thickness 726 of each ofthe disks 218 of the illustrated example is the same. In this manner,the example disks 710-714 provide a gradient or varying crackingpressure. For example, the first disk 710 may have a cracking pressurethat is greater than the cracking pressure of the second disk 712 and/orthe third disk 714, and the second disk 712 may have a cracking pressurethat is greater than the cracking pressure of the third disk 714.However, in some examples, the thickness 726 of the first disk 710 maybe different than the thickness 726 of the second disk 712 and/or thethird disk 714, and/or the thickness 726 of the second disk 712 may bedifferent than the thickness 726 of the first disk 710 and/or the thirddisk 714. In some examples, each of the disks 710-714 may have the samecracking pressure. In some examples, the gradient of cracking pressuresof the disks 710-714 may be reversed from a lower cracking pressure to ahigh cracking pressure. For example, the first disk 710 may have acracking pressure that is less than the cracking pressure of the seconddisk 712 and/or the third disk 714, and the second disk 712 may have acracking pressure that is less than the cracking pressure of the thirddisk 714.

The disks 218 of the illustrated example may have different diameters orradii relative to a longitudinal axis 728 of the pylon 702. For example,the first disk 710 of the illustrated example has a radius that is lessthan a radius of the second disk 712 and/or the third disk 714, and thesecond disk 712 has a radius that is less than the radius of the thirddisk 714. For example, the first disk 710 of the illustrated exampleincludes a radius that is slightly less than the radius R₁ of theexample first valve seat 604 (FIG. 6), the second disk 712 of theillustrated example includes a radius that is (e.g., slightly) less thanthe radius R₂ of the example second valve seat 606 (FIG. 6), and thethird disk 714 of the illustrated example includes a radius that is(e.g., slightly) less than the radius R₃ of the example third valve seat606 (FIG. 6). However, in other examples, each of the disks 218 may havethe same radius.

The head 704 of the illustrated example couples the flow control member216 (e.g., the pylon and the disks 218) to the fluid apparatus 100. Inparticular, the annular wall 730 of the illustrated example includes anouter surface having threads 734 to engage the threads 406 of the firsthousing portion 204 (FIGS. 2 and 4). In some examples, the threads 734of the head 704 are similar to (e.g., the same as) the threads 406 ofthe first housing portion 204. Additionally, as described in greaterdetail below, to adjust (e.g., increase or decrease) a pre-load to thedisks 218, the flow control member 216 adjusts relative to thelongitudinal axis 318 of the first housing portion 204 via the head 704.

To enable fluid flow through the head 704, the head 704 of theillustrated example includes an airfoil 736. More specifically, theairfoil 736 of the illustrated example has a spoke pattern providing aplurality of ribs 738 (e.g., spokes) positioned between a plurality ofpassageways 740. The ribs 738 and the passageways 740 of the illustratedexample are radially spaced relative to the longitudinal axis 728. Thepassageways 740 and the ribs 738 of the illustrated example extendbetween a first end 742 of the head 704 and a second end 744 of the head704 opposite the first end 742. Each of the ribs 738 of the illustratedexample separates (e.g., isolates) two adjacent passageways 740. Theribs 738 provide structural support (e.g., rigidity) to the head 704and, more generally, to the flow control member 216. For example, theribs 738 prevent the flow control member 216 and/or the pylon 702 fromtwisting about the longitudinal axis 728 during operation. In theillustrated example, the head 704 is cylindrically shaped and has adiameter that is greater than a diameter of the pylon 702. The head 704of the illustrated example has a diameter that is larger than thediameter at the first end 706 of the pylon 702. The ribs 738 of theillustrated example attach the annular wall 730 to an outer surface ofthe pylon 702. To promote laminar flow characteristic(s) through thepassageways 740, the ribs 738, the annular wall 730 and a wall of thepylon 702 of the illustrated example employ an airfoil shape having acurved leading edge and a sharp trailing edge as described in greaterdetail in FIGS. 8A-8E.

FIG. 8A is a cross-sectional view of one of the passageways 740 of theexample head 704 of FIGS. 7A and 7B. Each of the passageways 740 of thehead 704 of the illustrated example has an airfoil profile 802. Morespecifically, the airfoil profile 802 of the passageways 740 includes aquarter-chord 804 adjacent the first end 742 of the head 704 (e.g.,oriented toward the inlet 210 (FIG. 2)) and a trailing edge 806 adjacentthe second end 744 of the head 704 (e.g., oriented toward the outlet 212(FIG. 2)). In particular, the airfoil profile 802 provides or induceslaminar fluid flow characteristic(s) and/or prevents or reducesturbulent fluid flow characteristic(s) as fluid flows through thepassageways 740. In other words, the airfoil profile 802 prevents orreduces flow separation from an inner surface 808 of the passageways 740when fluid flows through each of the passageways 740. In some examples,one or more of the passageways 740 may include a substantially straightflow path (e.g., a passageway without the airfoil profile 802) and/ormay include any other shape or profile.

FIG. 8B is a partial, perspective view of the example flow controlmember 216 of FIGS. 1-6, 7A, 7B and 8A. FIG. 8C is another partial,perspective view of the example flow control member 216 of FIGS. 1-6,7A, 7B and 8A. FIG. 8D is a cross-sectional view of one of the ribs 738of FIGS. 1-6, 7A, 7B and 8A-8C. Referring to FIGS. 8A-8D, each of theexample ribs 738 has a body 810. The body 810 of each of the ribs 738 ofthe illustrated example has an airfoil profile 812 (e.g., a graduallynarrowing or tapering profile, an aerodynamic profile, etc.) between afirst end 814 of the body 810 and a second end 816 of the body 810. Forexample, the body 810 of the illustrated example gradually convergestoward the second end 816. For example, the first end 814 has a curvedleading edge that converges to a sharp trailing edge at the second end816. The first end 814 of the body 810 is oriented toward the inlet 210(FIG. 2) and is adjacent the first end 742 of the head 704 and thesecond end 816 of the body 810 is oriented toward the outlet 212 (FIG.2) and is adjacent the second end 744 of the head 704. The first end 814of the body 810 of the illustrated example has a first dimension 818(e.g., a thickness) that is greater than a second dimension 820 (e.g., athickness) of the second end 816 of the body 810. In addition, the firstend 814 of the body 810 has an arcuate or curved surface or shape 822.

FIG. 8E is side view of the example flow control member 216 of FIGS. 1,2, 7A, 7B and 8A-8C. Referring to FIG. 8E, the first end 814 of the body810 of each of the rib 738 tapers or is angled between the pylon 702 andthe annular wall 730. For example, a first lateral edge 824 of the body810 adjacent (e.g., coupled to) the pylon 702 is elevated by a distance826 (e.g., a vertical distance) relative to a second lateral edge 828 ofthe body 810 adjacent (e.g., coupled to) the annular wall 730. In otherwords, in the orientation of FIG. 8E, the first lateral edge 824 isabove or raised relative to the second lateral edge 828. For example,the first end 814 of the body 810 has a tapered profile 830 between thepylon 702 and the annular wall 730. In the illustrated example, thesecond lateral edge 828 terminates at the annular wall 730. In someexamples, the second lateral edge 828 is substantially flush with thefirst end 742 of the head 704. Referring to FIGS. 8A-8D, the profile 802the passageways 740 and/or the profile 812 of the example ribs 738 ofthe head 704 of the illustrated example promote laminar flowcharacteristics and/or prevent formation of turbulent flowcharacteristics when fluid flows across the head 704 via the passageways740.

FIG. 9 is another cross-sectional, perspective view of the example fluidapparatus 100 of FIGS. 1-6, 7A-7B, and 8A-8E. To assemble the examplefluid apparatus 100, the head 704 of the flow control member 216 iscoupled to the first housing portion 204 via threads). The head 704 ofthe flow control member 216 couples (e.g., fastens) to the first housingportion 204 via the threads 734 of the annular wall 730 and the threads406 of the first housing portion 204.

To provide and/or adjust (e.g., increase or decrease) a preload on thedisks 218, the flow control member 216 of the illustrated exampleadjusts (e.g., rectilinearly) along the longitudinal axis 214. Forexample, adjusting a position of the flow control member 216 in adirection along the longitudinal axis 214 adjusts (e.g., increases ordecreases) a compression force imparted to the disks 218, which causesthe disks 218 to impart a sealing force against the respective valveseats 220. In some examples, the head 704 of the flow control member 216is rotated about the longitudinal axis 214 and moved to a positioncorresponding to a desired cracking pressure of the fluid apparatus 100(e.g., a cracking pressure of the first disk 710). For example, aposition of the head 704 closer toward the inlet 210 provides a greateramount of compression force to the disks 218 to enable the disks 218 toseal tighter against the respective valve seats 220 than a position ofthe head 704 closer toward the outlet 212. In some examples, the firstdisk 710 of the illustrated example may have the smallest surface areaand, thus, the head 704 may be positioned to provide a preloadassociated with the cracking pressure of the first disk 710. In someexamples, due to the threads 734 and the threads 406, the crackingpressures of the disks 218 can be continuously adjusted between aninitial threaded position (e.g., provided at a first end of the threads406) and a final threaded position (e.g., provided at a second end ofthe threads 406 opposite the first end).

A preload (e.g., the compression force provided to the disks 218) maycorrespond to a desired cracking pressure (e.g., 90pounds-per-square-inch (psi)) of the fluid apparatus 100. In theillustrated example, the cracking pressure may be a minimum upstreampressure at the inlet 210 (FIG. 2) that causes the disks 218 to move toan open position (e.g., the disks 218 deflect away from the respectivevalve seats 220) to allow fluid flow between the inlet 210 and theoutlet 212 through the fluid flow passageway 208. Thus, the examplefluid apparatus 100 of the illustrated example provides a preload to theflow control member 216 without use of a biasing element such as, forexample, a spring. In some examples, a position of the head 704corresponding to a specific preload may be determined experimentallyand/or provided via tables. The experimentally determined preloadcorresponding to head position may be based on, for example, thethickness 726 of the disks 218, a radius of the disks, a material of thedisks, and/or any other factor(s) or characteristic(s). In some suchexamples, the head 704 may be rotated about the longitudinal axis 214 toposition the head 704 at a specific position that provides the desiredpreload or cracking pressure.

In some examples, after the head 704 is positioned to provide a desiredcracking pressure to the disks 218, a fastener 902 may be employed tosecure a position of the head 704 along the longitudinal axis 214. Forexample, the head 704 may be secured to the first housing portion 204via the fastener 902 to prevent rotation of the head 704 relative to thefirst housing portion 204 (e.g., the head 704 backing out via thethreads 734) due to, for example, vibration imparted to the fluidapparatus 100 during operation. The fastener 902 may include, forexample, a weld-tack, a locking ring, a cryo-locktite, a pin, a chemicalfastener (e.g., adhesive), C-ring, an S-ring, and/or any other lock orfastener to prevent movement or rotation of the head 704 relative to thefirst housing portion 204 about the longitudinal axis 214.

After the flow control member 216 is coupled to the first housingportion 204, the second housing portion 206 is coupled to the firsthousing portion 204. When the second housing portion 206 is coupled tothe first housing portion 204, the disks 218 of the flow control member216 engage the respective valve seats 220. In some examples, each of thedisks 218 matably engages the respective one of the valve seats 220. Inaddition, the surface finishes of the sealing surfaces of the disks 218and/or the valve seats 220 improve sealing between the disks 218 and thevalve seats 220. In the illustrated example, the fasteners 207 couplethe first housing portion 204 and the second housing portion 206 via theflanges 308 and 504. In the illustrated example, the holes 316 and 512of the respective flanges 308 and 504 align to receive the fasteners207.

In some examples, to trap particulates in a fluid flowing through thefluid apparatus 100, one or more filters may be positioned in the fluidflow passageway 208. In some examples, a filter may positioned adjacentthe inlet 210 and/or the outlet 212. The filter may be, for example, a10-15 micron filter. In sonic examples, the filter may be formed withthe fluid apparatus 100 (e.g., via injection molding, additivemanufacturing, etc.). The filter may span the fluid flow passageway 208(e.g., across a diameter of the fluid flow passageway 208). The filtermay capture, for example, particulate contained in a fluid and/orparticulate that may flake off the disks 218 (e.g., due to the disks 218fluttering).

Alternatively, in some examples, the first housing 202 does not includethe threads 406. In some such examples, one or more guides or slots areformed in the cavity 402 (e.g., along the inner surface 404) of thefirst housing 204 and/or the inner surface 618 of the second housing206. In some such examples, the head 704 and/or the flow control member216 includes one or more rails to slidably engage a respective guide orslot. In some examples, the rails and/or the slots may include a lock(e.g., protrusions, spring-loaded button and opening, a pin and holeconfiguration, etc. and/or any other fastener to lock a position of therails relative to the guides. In some such examples, the lock may bepositioned at a plurality of depths or locations (e.g., discretelocations) along the guides and/or the rails. In some such examples, thelock may be positioned at any one of the discrete locations or depthscorresponding to a desired preload of the disks 218. In some suchexamples, the guide and rail configuration provides a snap-in connectionor interface between the flow control member 216 and the first housing204 and/or the second housing 206.

Alternatively, in some examples, the flow control member 218 is threadedto the first housing 204 via the threads 406 a fully threaded positionto a fully upward position in the orientation of FIG. 9. In some suchexamples, the position of the flow control member 216 provides a preloadto the disks 218 when the second housing 206 is coupled to the firsthousing 204. A dimensional length of the body 702 (e.g., along thelongitudinal axis 728 between the second end 744 of the head 704 and thetip 708 of the body 702) may be varied during manufacturing to providedifferent sets of preloads and/or cracking pressures. In some suchexamples, an array of different sizes of the flow control member 216 maybe provided to vary the cracking pressures of the disks 218. Forexample, the cracking pressures of the disks 218 may be dependent on alength of the flow control member 216.

FIG. 10 is a cross-sectional view of the fluid apparatus 100 of FIGS.1-6, 7A-7B, 8A-8E and 9 shown in a closed position 1000 (e.g., a fullyclosed position). In operation, when a pressure differential across thedisks 218 is less than a cracking pressure of the disks 218, the disks218 move to the closed position 1000 (e.g., to seal against therespective valve seats 220) to prevent fluid flow through the fluid flowpassageway 208 from the inlet 210 to the outlet 212. For example, when afluid pressure at the inlet 210 is less than a cracking pressure of thedisks 218 (e.g., a force or preload imparted to the second end 724 ofthe disks 218 by the position of the head 704), the first face 722 ofthe respective disks 218 remain engaged or in sealing engagement withthe respective valve seats 220 to prevent fluid flow between the inlet210 and the outlet 212 via the fluid flow passageway 208. In otherwords, the disks 218 engage the respective valve seats 220 to provide atight seal (e.g., a leak proof seal) to prevent fluid from flowing orpassing across the valve seats 220 when the fluid apparatus 100 is inthe closed position 1000. Additionally, the disks 218, in the closedposition 1000, prevent fluid from flowing from the outlet 212 toward theinlet 210 (e.g., reverse fluid flow) when, for example, a fluid pressureat the outlet 212 is greater than a fluid pressure at the inlet 210. Inother words, the disks 218 provide a tight seal (e.g., leak proof seal)to prevent reverse fluid flow from the outlet 212 to the inlet 210.

Additionally, the example flow control member 216 provides redundantsealing. In particular, if the first disk 710 fails and allows fluid toflow past the first valve seat 604 when the fluid apparatus 100 is inthe closed position 1000, the second disk 712 and/or the third disk 714remain in sealing engagement with the respective valve seats 606 and 608when the fluid pressure is less than the cracking pressures of therespective second and third disks 712 and 714, thereby maintaining thefluid apparatus 100 in the closed position 1000.

FIG. 11 is a cross-sectional view of the example fluid apparatus 100shown in an open position 1100 (e.g., a fully open position). Inoperation, a pressure differential across the disks 218 that is greaterthan a cracking pressure of the disks 218 causes the disks 218 to moveto the open position 1100 (e.g., move or deflect away from therespective valve seats 220) to allow fluid flow through the fluid flowpassageway 208 from the inlet 210 to the outlet 212. More specifically,a fluid pressure at the inlet 210 is greater than a cracking pressure ofthe first disk 710 (e.g., a fluid pressure imparted to the first face722 of the first disk 710 that is greater than the preload forceimparted to the second face 724 by the flow control member 216) causesthe peripheral edge 718 of the first disk 710 to deflect away from thefirst valve seat 604 to allow fluid flow to flow through an orifice 1102defined by the first valve seat 604. In the illustrated example, thefluid flows to a first chamber 1104 between the first disk 710 and thesecond disk 712.

When the fluid reaches the second disk 712, a fluid pressure greaterthan a cracking pressure of the second disk 712 (e.g., a fluid pressureimparted to the first face 722 of the second disk 712 that is greaterthan the preload force imparted to the second face 724 of the seconddisk 712 by the flow control member 216) causes the peripheral edge 718of the second disk 712 to move or deflect away from the second valveseat 606 to allow fluid flow through an orifice 1106 defined by thesecond valve seat 606. In the illustrated example, the fluid flows fromthe first chamber 1104 to a second chamber 1108 between the second disk712 and the third disk 714. Similarly, when the fluid reaches the thirddisk 714, a fluid pressure greater than a cracking pressure of the thirddisk 714 (e.g., a fluid pressure imparted to the first face 722 of thethird disk 714 that is greater than the preload force imparted to thesecond face 724 of the third disk 714 by the flow control member 216)causes the peripheral edge 718 of the third disk 714 to move or deflectaway from the third valve seat 608 to allow fluid flow through anorifice 1110 defined by the third valve seat 608 and toward thepassageways 740 of the head 704. The fluid then flows to the outlet 212.

In the illustrated example, the disks 218 provide a gradually decreasingcracking pressure from the first disk 710 to the third disk 714. Thus,the fluid apparatus 100 moves to the open position 1100 when a fluidpressure is greater than a cracking pressure of the first disk 710. Insome examples, the disks 218 may be configured to provide a progressiveor gradually increasing cracking pressure from the first disk 710 to thethird disk 714. In other words, a fluid pressure may cause the firstdisk 710 and/or the second disk 712 to move to an open position (e.g.,deflect away from the respective valve seats 604 and 606), but the fluidpressure may not cause third disk 714 to move to an open position if thefluid pressure is less than a cracking pressure of the third disk 714.

In some examples, when the cracking pressure of the first disk 710 isgreater than the cracking pressures of the second disk 712 and the thirddisk 714, the disks 218 may not move to their respective open positionssimultaneously. In some such instances, when fluid enters the firstchamber 1104, a pressure of the fluid may decrease to a pressure belowthe cracking pressure of the second disk 712. Thus, even if the pressureof the fluid upstream from the first disk 710 is greater than a crackingpressure of the second disk 712, the fluid may not cause the second disk712 to open when the pressurized fluid enters the first chamber 1104(e.g., due to hysteresis). The second disk 712 may delay opening to anopen position until the pressure of the fluid in the first chamber 1104increases recovers) to a pressure above the cracking pressure of thesecond disk 712. Thus, in some instances, the fluid apparatus 100 mayprovide a lag or delay in opening the second disk 712 and/or the thirddisk 714. Such delay may be provided, reduced and/or eliminated byadjusting a characteristic of the fluid apparatus 100 such as, forexample, the distances (e.g., vertical distances) between the disks 218(e.g., distances D1, D2 and D3), the distances (e.g., verticaldistances) between the valve seats 220 (e.g., distances L2 and L2), thethicknesses of the disks 218, and/or the diameters of the disks 218. Insome instances, however, when the cracking pressure of the first disk710 is greater than the cracking pressures of the second disk 712 andthe third disk 714, the disks 218 may move to their respective openpositions simultaneously. In some examples, the characteristic such as,for example, the distances (e.g., vertical distances) between the disks218 (e.g., distances D1 D2 and D3), the distances (e.g., verticaldistances) between the valve seats 220 (e.g., distances L2 and L2), thethicknesses of the disks 218, and/or the diameters of the disks 218 canbe adjusted or modified to enable simultaneous movement of the disks218. In some examples, posts or pillars (e.g., pillars 1632 and 1634 ofFIG. 16C) may be employed to enable simultaneous movement of the disks218.

Additionally, when the peripheral edges 718 of the disks 218 deflect ormove away from the respective valve seats 220 (e.g., to an openposition), the disks 218 have a curved or arcuate profile (e.g., asmooth curve without a kink or sharp edge). In other words, the arcuateprofile provides a continuously smooth surface and does not produce orform a fold or kink in the first face 722 of the disks 218 when theperipheral edge 718 is in a deflected or open position (e.g., spaced ordeflected away from the valve seats 220). The relatively smooth orarcuate profile of the disks 218 when deflected away from the respectivevalve seats 220 promotes laminar flow characteristic(s) and/or preventsformation of turbulent flow as the fluid flows across the first face 722of the respective disks 218. Additionally, the airfoil profile 802 (FIG.8A) of the passageways 740 and/or the profile 812 of the ribs 738 (FIG.8D) may promote laminar flow characteristic(s) and/or prevent formationof turbulent flow characteristic(s) as the fluid flows through thepassageways 740 and toward the outlet 212.

To monitor a characteristic of a fluid flowing through the passageway208, the fluid apparatus 100 of the illustrated example employs one ormore sensors 1112. For example, the sensors 1112 may monitor or detect apressure of a fluid, a temperature of a fluid, a velocity of a fluid,and/or any other characteristic of a fluid flowing through the fluidflow passageway 208. The sensors 1112 may be positioned within the fluidflow passageway 208 of the fluid apparatus 100. For example, a firstsensor 1112 a may be positioned in the first chamber 1104, a secondsensor 1112 b may be positioned in the second chamber 1108, a thirdsensor 1112 c may be positioned upstream from the first valve seat 604,and/or a fourth sensor 1112 d may be positioned downstream from thethird valve seat 608. The sensors 1112 may include pressure transducers,a piezoelectric sensor and/or any other suitable sensor(s). The sensors1112 may be formed with or coupled to an inner surface of the fluid flowpassageway 208 via, for example, injection molding, additivemanufacturing process(es), fasteners (e.g., chemical or mechanical),and/or any other process(es).

FIGS. 12-16 illustrate other example fluid apparatus 1200-1600 disclosedherein. Those components of the example fluid apparatus 1200-1600 thatare substantially similar or identical to the components of the examplefluid apparatus 100 described above in connection with FIGS. 1-6, 7A-7B,8A-8E, and 9-11 and that have functions substantially similar oridentical to the functions of those components will not be described indetail again below. Instead, the interested reader is referred to theabove corresponding descriptions. To facilitate this process, similarreference numbers will be used for like structures.

Referring to FIG. 12, the example fluid apparatus 1200 includes a valvebody 1202 defining a fluid flow passageway 1204 having a plurality ofvalve seats 1206 between an inlet 1208 and an outlet 1210. Unlike thehousing 202 of the example fluid apparatus 100 of FIGS. 1-6, 7A-7B,8A-8E, and 9-11, the valve body 1202 of the example fluid apparatus 1200is formed as a unitary piece or structure. The flow control member 216is coupled to the valve body 1202 via the threads 734 of the head 704.For example, the flow control member 216 is positioned in the fluid flowpassageway 208 from the outlet 1210 and fastened to the valve body 1202.

The example fluid apparatus 1300 of FIG. 13 is shown in a closedposition 1301 on the left side of the FIG. 13 and an open position 1303on the right side of FIG. 13. The fluid apparatus 1300 of theillustrated example includes a valve body 1302 defining a fluid flowpassageway 1304 between an inlet 1306 and an outlet 1308. An outersurface 1310 of the valve body 1302 includes a first threaded portion1312 adjacent the inlet 1306 to couple the fluid apparatus 1300 to anupstream source (e.g., the upstream source 102 of FIG. 1) and a secondthreaded portion 1314 adjacent the outlet 1308 to couple the fluidapparatus 1300 to a downstream source (e.g., the downstream source 106of FIG. 1). The valve body 1302 includes a threaded annular wall 1316projecting from an inner wall 1318 of the fluid flow passageway 1304.

A plurality of disks 1320 are positioned in the fluid flow passageway1304. In particular, each of the disks 1320 includes an outer peripheraledge 1322 and an inner edge 1324 defined by a center opening 1326. Morespecifically, the peripheral edge 1322 is fixed or attached to (e.g.,integrally formed with) the inner wall 1318 of the valve body 1302defining the fluid flow passageway 1304 and the inner edge 1324 of thedisks 1320 is free to deflect or move. The disks 1320 of the illustratedexample project from the inner wall 1318 towards a longitudinal axis1328 of the valve body 1302. A first disk 1330 has a first dimension(e.g., a diameter), a second disk 1332 has a second dimension adiameter) and a third disk 1334 has a third dimension diameter), wherethe first dimension is less than the second dimension and the thirddimension, and the second dimension is less than the third dimension.

A poppet or flow control member 1336 is coupled to the valve body 1302and positioned in the fluid flow passageway 1304. To couple to the valvebody 1302, the flow control member 1336 of the illustrated exampleincludes a threaded portion 1305 to engage the threaded annular wall1316. The flow control member 1336 includes a body 1338 positionedthrough the center opening 1326 of the respective disks 1320. Inparticular, the body 1338 of the example flow control member 1336includes a conical or stepped profile to define a plurality of valveseats 1340 to be engaged by a respective one of the disks 1320. Forexample, the body 1338 of the flow control member 1336 of theillustrated example includes a first valve seat 1342, a second valveseat 1344, and a third valve seat 1346 spaced along the body 1338. Thefirst disk 1330 is to engage or seal against the first valve seat 1342,he second disk 1332 is to engage or seal against the second valve seat1344, and the third disk 1334 is to engage or seal against the thirdvalve seat 1346 when the fluid apparatus is in a closed position toprevent fluid flow from the inlet 1306 to the outlet 1308.

To support the flow control member 1336 and/or to reduce vibration tothe flow control member 1336, the example fluid apparatus 1300 of theillustrated example includes supports 1348. The supports 1348 arecoupled to or engage (e.g., frictionally engage) the flow control member1336 to prevent movement or rotation of the body 1338 relative to thelongitudinal axis 1328 due to, for example, vibration. The supports 1348of the illustrated example include passageways 1350 to enable fluid flowthrough the supports 1348. In some examples, the passageways 1350 mayemploy an airfoil profile similar to the passageways 740 of FIGS. 7A and7B.

In some examples, an example valve disclosed herein may be a hybrid orcombination of the poppet of FIG. 12 and the valve body of FIG. 13. Forexample, a hybrid valve may be configured to provide disks spacedrelative to a longitudinal axis of a valve body, where at least a firstdisk is attached to the valve body and at least a second disk isattached to the poppet. For example, the valve body 1302 of FIG. 13 maybe configured with valve seats 1206 to receive the respective disks 218of the flow control member 216 of FIG. 12, and the flow control member216 of FIG. 12 may be configured with valve seats 1340 of FIG. 13 toreceive the corresponding disks 1320 of the valve body 1302 of FIG. 13.Thus, in some such examples, an example fluid apparatus may have one ormore disks (e.g., disks 1320) attached to a valve body that engage valveseats formed by a flow control member, and the fluid apparatus may haveone or more disks (e.g., disks 218) attached to the poppet that engagevalve seats formed by the valve body.

Referring to FIG. 14, the example fluid apparatus 1400 is shown in aclosed position 1401 on the left side of FIG. 14 and an open position1403 on the right side of FIG. 14. The fluid apparatus 1400 of theillustrated example includes a valve body 1402 having a plurality ofdisks 1404 (e.g., radially and longitudinally) spaced relative to alongitudinal axis 1406 of a fluid flow passageway 1408. A flow controlmember 1410 is supported in the fluid flow passageway 1408 via a firstsupport 1412 adjacent an inlet 1414 and a second support 1416 adjacentan outlet 1418. The first support 1412 and the second support 1416include passageways 1420 to allow fluid flow through the fluid flowpassageway 1408 between the inlet 1414 and the outlet 1418. The flowcontrol member 1410 includes valve seats 1422 to be engaged by therespective disks 1404. In particular, the valve seats 1422 have avarying dimension (e.g., a varying diameter and/or are sloped orangled). In this manner, the disks 1404 seal against the valve seats1422 when the disks 1404 deflect toward the inlet 1414 to prevent fluidflow through the fluid flow passageway 1408. The disks 1404 deflect awayfrom the valve seats 1422 when the disks 1404 deflect toward the outlet1418 to allow fluid flow through the fluid flow passageway 1408. Unlikethe example fluid apparatus 100, 1200 and 1300 of FIGS. 1-13, the fluidapparatus 1400 of the illustrated example provides a non-adjustable ornon-tuning preload to the disks 1404.

Referring to FIG. 15, the example fluid apparatus 1500 is substantiallysimilar to the fluid apparatus 100 of FIGS. 1-11 except the fluidapparatus 1500 does not provide redundant sealing. More specifically,the example fluid apparatus 1500 of the illustrated example includes avalve body 1502 having only one valve seat 1504 and a flow controlmember 1506 having only one disk 1508.

Referring to FIG. 16A, the example fluid apparatus 1600 is substantiallysimilar to the fluid apparatus 100 of FIGS. 1-11. The example fluidapparatus 1600 of FIGS. 16 includes a housing 1602 having a firsthousing 1604 (e.g., an upper housing or bonnet) and a second housing1606 (e.g., a lower housing or valve body). In the illustrated example,the second housing 1606 includes threads 1608 along at least a portionof an inner surface 1610 of the second housing 1606. The threads 1608are to receive the head 704 of the flow control member 216. In thismanner, the flow control member 216 may be positioned or disposed in thesecond housing 1604 and/or adjusted (e.g., axially adjusted) relative tothe second housing 1606 to provide a cracking pressure to the disks 218.Thus, the fluid apparatus 1600 of the illustrated example is similar tothe fluid apparatus 100 except that the second housing 1606 includes thethreads 1608 and the first housing 1604 does not include threads (e.g.,the threads 406 shown in FIG. 4). For example, the second housing 1606of the illustrated example includes an inlet 210 (e.g., a fitting 508),valve seats 220, a flange 504 and seal glands 520 and 522. The firsthousing 1604 of the illustrated example includes, for example, a cavity402, a flange 304, a tapered portion 312, an outlet 212, and a fitting314. The second housing 1606 of the illustrated example has a length(e.g., an axial length in the direction of the longitudinal axis 214)that is greater than a length of the first housing 1604 (e.g., an axiallength in the direction of the longitudinal axis 214). However, in someexamples, a length of the first housing 1604 may be greater than orequal to a length of the second housing 1606. The fastener 902 (see FIG.9) may be provided on the second side of the head 704 to secure aposition f the flow control member 216 relative to the second housing1606 once the flow control member 216 is adjusted to provide a desiredcracking pressure. In some examples, the fluid apparatus 1600 of FIG. 16facilitates placement of the fastener 902 (e.g., a C-ring) to maintainor lock a position of the head 704. In some examples, a spacer may beprovided between the respective valve seats between the sealing surfaceof the valve seats 220) and the disks 218 (e.g., the sealing surface ofthe disks 218) to prevent or reduce abrasion between (e.g., the sealingsurfaces of) the valve seats 220 and the disks 218 when the flow controlmember 216 rotates relative to the longitudinal axis 214. In someexamples, the spacer may be wax or a cloth. After the flow controlmember 216 is coupled to the second housing 1606, the spacer is removed.For example, the wax may be melted and/or the cloth may be burned aftera position of the flow control member 216 is positioned to provide thedesired cracking pressures of the disks 218.

FIG. 16B illustrates another example flow control member 1620 disclosedherein that may implement the example fluid apparatus 1600 of FIG. 16A(or any other flow control member of the example fluid apparatusdisclosed herein). For example, the flow control member 1620 of FIG. 16Bmay replace the flow control member 216 of FIG. 16A. The flow controlmember 1620 is substantially similar to the flow control member 216 ofFIGS. 2-6, 7A-7B, 8A-8D and 9-11. For example, the flow control member1620 includes a pylon 702, a plurality of disks 218 and a head 704. Thehead 704 of the illustrated example is configured with a tool receivingportion 1622 to receive a tool or other rotating apparatus (e.g., anactuator). The tool receiving portion 1622 of the illustrated exampleprotrudes from an upper surface 1624 of the second end 744 of the head704 and/or the pylon 702. The tool receiving portion 1622 enablesrotation of the head 704 relative to a longitudinal axis 214 (e.g.,relative to the second housing 1606). For example, the tool receivingportion 1622 enables rotation of the flow control member 1620 (e.g., viathe head 704) to adjust a cracking pressure of the flow control member216 (e.g., the disks 218). For example, in some instances, a Modulus ofElasticity of the disks 218 may be relatively high such that rotation ofthe head 704 of one degree relative to the longitudinal axis 214 of thefluid apparatus 1600 may cause a 5-fold increase in the crackingpressure of the disks 218. The tool receiving portion 1622 of theillustrated example enables relatively smaller rotations betweenapproximately 0.01 degree and less than 1 degree) of the head 704relative to the longitudinal axis 214 to enable fine tune adjustment(e.g., small increments of cracking pressure such as 1pound-per-square-inch (psi)).

The example tool receiving portion 1622 of the illustrated example has agear profile 1626 to engage a gear face or profile of a tool to enablefine tune adjustment of the flow control member 216. For example, thegear profile 1626 includes gear teeth radially spaced relative to thelongitudinal axis 214. In some examples, the tool receiving portion 1622and/or the second end 744 of the head 704 and/or the pylon 702 mayinclude a Hex profile, a star profile, and/or any other profile toreceive a tool (e.g., a Hex key) to enable rotation of the head 704relative to the longitudinal axis 214. Thus, the example fluid apparatus1600 of FIG. 16 may facilitate adjustment of the flow control member 216to adjust a desired cracking pressure.

In some examples, the fluid apparatus 1600 may employ an actuator tomove or rotate the fluid control member 216. For example, the actuatormay be a rotary actuator, a linear actuator, an electric motor, apneumatic actuator, a hydraulic actuator and/or any other device torotate the flow control member 216 about the longitudinal axis 214. Insome examples, the actuator may be positioned inside the fluid flowpassageway 208. In some examples, the actuator may be coupled externallyrelative to the fluid apparatus 100. In some examples, the actuator maybe a rotary actuator operatively coupled (e.g., via an actuator stem) tothe tool receiving portion 1622. In some examples, an actuator mayinclude a linear actuator to move a rack operatively coupled to the gearprofile to rotate of the flow control member 216 relative thelongitudinal axis 214. In some examples, the actuator may be an electricmotor (e.g., positioned in the fluid flow passageway 208 or outside ofthe housing 202) that has an output shaft operatively coupled (e.g.,directly or indirectly via gears or a transmission) to rotate the flowcontrol member 216. In some such examples, the motor may provideregeneration when a vibration induced rotation causes the flow controlmember 216 to rotate the motor (e.g., back drive the motor).

FIG. 16C illustrates another example flow control member 1630 disclosedherein that may implement the example fluid apparatus 1600 of FIG. 16A(or any other flow control member of the example fluid apparatusdisclosed herein). For example, the flow control member 1630 of FIG. 16Cmay replace the flow control member 216 of the example fluid apparatus100 or the example fluid apparatus 1600. The flow control member 1630 issubstantially similar to the flow control member 216 of FIGS. 2-6,7A-7B, 8A-8D and 9-11. For example, the flow control member 1630includes a pylon 702, a plurality of disks 218 and a head 704. Theexample flow control member is substantially similar to the flow controlmember 216 except that it includes legs or pillars 1632 and 1634. Thepillars 1632 and 1634 enable simultaneous operation of the disks 218when the disks 218 move between the open position and the closedposition relative to the valve seats 220.

For example, the pillars 1632 of the illustrated example extend betweena second side 724 of a first disk 710 and a first side 722 of a seconddisk 712, and the pillars 1634 of the illustrated example extend betweena second side 724 of the second disk 712 and a first side 722 of a thirddisk 714. In particular, each of the pillars 1632 and 1634 define alongitudinal axis 1636 extending between first end 1638 and a second end1640. In the illustrated example, the first end 1638 of the pillars 1632is integrally formed or attached to the second side 724 of the firstdisk 710 and the second end 1640 is integrally formed or attached to thefirst side 722 of the second disk 712. Similarly, the first end 1638 ofthe pillars 1634 is integrally formed or attached with the second side72.4 of the second disk 712 and the second end 1640 of the pillars 1634is integrally formed or attached to the first side 722 of the third disk714.

The pillars 1632 and 1634 of the illustrated example are radially spacedrelative to the longitudinal axis 214. In some examples, the flowcontrol member 1630 may include two pillars 1632 and/or 1634 that areradially spaced relative to the longitudinal axis 214 at an angle ofapproximately 180 degrees. In some examples, the flow control member1630 may include three pillars 1632 and/or 1634 that are radially spacedrelative to the longitudinal axis 214 at an angle of approximately 120degrees. In some examples, the flow control member 1630 may include aplurality of pillars 1632 and/1634 that may be radially spaced at anangle of between approximately 30 degrees and 60 degrees relative to thelongitudinal axis 214. In some examples, the flow control member 1630may include only one pillar 1632 and/or 1634.

The longitudinal axis 1636 of the pillars 1632 and/or 1634 of theillustrated example are substantially parallel relative to thelongitudinal axis 214. However, in some examples, the pillars 1632and/or 1634 may be positioned non-parallel (e.g., at an angle greaterthan zero) relative to the longitudinal axis 214. For example, thelongitudinal axis 1636 of the pillars 1632 and/or 1634 may be at anon-parallel angle relative to the longitudinal axis 214. For example,an example angle between the longitudinal axis 1636 of the pillars 1632and/or 1634 relative to the longitudinal axis 214 may be betweenapproximately 1 degree and 60 degrees.

In operation, the pillars 1632 and 1634 enable simultaneous movement ofthe first disk 710, the second disk 712 and the third disk 714. Inparticular, the pillars 1632 and 1634 reduce or eliminate a delay of thefirst disk 710, the second disk 712 and the third disk 714 moving totheir respective open positions due to pressure drops experienced in thechambers 1104 and 1108 noted above in connection with FIG. 11. Thus, thepillars 1632 and 1634 reduce or delay pressure (or flow-rate) changebetween upstream and downstream sections (e.g., between the chambers1104 and 1108) of the fluid apparatus 100 by allowing the disks 218 tosimultaneously open, as opposed to allowing each chamber 1104 and 1108to fill with fluid before the third disk 714 moves to an open position.

Thus, when one of the first disk 710, the second disk 712 or the thirddisk 714 moves to an open position or a closed position relative to thevalve seats 220, the other ones of the first disk 710, the second disk712 or the third disk 714 move simultaneously to their respective openpositions or closed positions. For example, when the pressure of thefluid provided at the first side 722 of the first disk 710 is greaterthan a cracking pressure of the first disk 710, the first disk 710 movesto an open position to allow fluid past the first disk 710. When thefirst disk 710 moves or deflects to an open position (e.g., an upwardposition in the orientation of FIG. 16C), the pillars 1632 cause thesecond disk 712 to deflect or move to an open position, and the pillars1634 cause the third disk 714 to deflect or move to an open position.Similarly, when the first disk 710 moves to a closed position relativeto the valve seat 220, the second disk 712 and the third disk 714 alsomove to the closed position relative to their respective valve seats220.

FIG. 16D illustrates another example flow control member 1650 disclosedherein that may implement the example fluid apparatus 1600 of FIG. 16A(or any other flow control member of the example fluid apparatusdisclosed herein). For example, the flow control member 1650 of FIG. 16Dmay replace the flow control member 216 of the example fluid apparatus100 or the example fluid apparatus 1600. The flow control member 1650 issubstantially similar to the flow control member 1630 of FIG. 16C, butformed with different pillars 1652 and 1654. In particular, the pillars1652 and 1654 of the illustrated example have a varying flexibility orstiffness characteristic(s). For example, the pillars 1652 and 1654 havea first flexibility or stiffness characteristic and a second flexibilityor stiffness characteristic different than the first flexibility orshiftless characteristic. For example, the pillars 1652 and 1654 arerelatively flexible when disks 218 are in the closed position (e.g.,sealingly engaged with the valve seats 220) and are relatively stiffwhen the disks crack toward the open position. For example, the pillars1652 and 1654 increase in stiffness during compression of the pillars1652 and 1654 such that the disks 218 are more flexible than the pillars1652 and 1654 when the disks 218 move or deflect toward the openposition (e.g., move away from the valve seats 220). As a result, thefirst flexibility or stiffness characteristic of the example pillars1652 and 1654 compensate for machining or manufacturing tolerances orerrors between the disks 218 (e.g., distances D1, D2 and D3 in FIG. 7A)and the valve seats 220 (e.g., distances L1, L2 and L3 in FIG. 6). Inother words, the first flexibility characteristic of the pillars 1652and 1654 compensate for a small differential in distance offset errorsor tolerances between the disks 218 and/or the valve seats 220 (e.g.,vertical distances). However, the second flexibility characteristicprovides sufficient stiffness during a large offset in distances (e.g.,during cracking of the first disk 710) to cause the disks 218 tosimultaneously move to their respective open positions relative to thevalve seats 220.

To provide varying compression and/or stiffness to the pillars 1652 and1654, the pillars 1652 and 1654 of the illustrated example are bent,curved or bowed between a first end 1658 and a second end 1660 of therespective pillars 1652 and 1654. More specifically, each of the pillars1652 and 1654 of the illustrated example include a pair of bows orstructures 1662 (e.g., a first bow 1662 a and a second bow 1662 b havingan arcuate profile). As the pair of bows 1662 compress, a center section1664 of each pair of bows 1662 becomes closer and, ultimately touch,thereby preventing further compression of the pair of bows 1662 andincreasing the stiffness of the pillars 1652 and 1654. As a result, theincrease in stiffness causes the pillars 1652 and 1654 to exert anupward force, causing the disks 218 to move simultaneously when thefirst disk 710 moves relative to the valve seat 220.

The pillars 1632 and/or 1634 of the example flow control member 1630,the pillars 1652 and/or 1654 of the example flow control member 1650,and/or the tool receiving portion 1622 of the example flow controlmember 1620 may be implemented with the other example flow controlmembers 218, 1320, 1404 and 1508 disclosed herein.

FIG. 17 illustrates an example method 1700 that may be used tomanufacture, fabricate and/or assemble an example fluid apparatusdisclosed herein such as the example fluid apparatus 100, 1200, 1300,1400, 1500 and/or 1600 of FIGS. 1-6, 7A-7B, 8A-8E, and 9-16. FIG. 18illustrates an example method 1800 that may be used to assemble anexample fluid apparatus disclosed herein such as the example fluidapparatus fluid apparatus 100, 1200, 1300, 1400, 1500 and/or 1600 ofFIGS. 1-6, 7A-7B, 8A-8E, and 9-16. FIG. 19 illustrates an example method1900 of operation of an example fluid apparatus disclosed herein such asthe example fluid apparatus 100, 1200, 1300, 1400, 1500 and/or 1600 ofFIGS. 1-6, 7A-7B, 8A-8E, and 9-16.

While an example of manufacturing, assembling and/or operating theexample fluid apparatus 100, 1200, 1300, 1400, 1500 and/or 1600 has beenillustrated in FIGS. 17, 18 and 19, one or more of the steps and/orprocesses illustrated in FIGS. 17, 18 and 19 may be combined, divided,omitted, eliminated, modified and/or implemented in any other way.Further still, the example methods of FIGS. 17, 18 and 9 may include oneor more processes and/or steps in addition to, or instead of, thoseillustrated in FIGS. 17, 18 and 19, and/or may include more than one ofany or all of the illustrated processes and/or steps. Further, althoughthe example method is described with reference to the flowchartsillustrated in FIGS. 17, 18 and 19, many other methods of manufacturing,assembling and/or operating the example fluid apparatus 100, 1200, 1300,1400, 1500 and/or 1600 of FIGS. 1-6, 7A-7B, 8A-8E, and 9-16 mayalternatively be used.

Referring to FIG. 17, the example method 1700 disclosed herein may beginby forming a first housing portion (block 1702), forming a secondhousing portion (block 1704), and forming a flow control member (block1706). In some examples, the second housing portion may be formed withone or more valve seats. In some examples, the flow control member maybe formed with one or more disks. In some examples, the example fluidapparatus 100, 1200, 1300, 1400, 1500 and/or 1600 disclosed herein maybe configured with on disk, two disks and/or more than three disks,respectively. In some examples, the example fluid apparatus 100, 1200,1300, 1400, 1500 and/or 1600 disclosed herein may be manufactured orformed via an additive manufacturing process (e.g., 3D printing),injection molding, machining, and/or any other suitable manufacturingprocess, and/or any combination thereof. Example additive manufacturingprocess(es) include, but are not limited to, direct metal lasersintering (DMLS), laser freeform manufacturing technology (LFMT),selective laser inciting (SLIM), fused deposition modeling (FDM), laserpuddle deposition (LPD), small puddle deposition (SPD), laser powder bed(LPB), electron beam powder bed (EBPD), indirect power bed (IPD), laserdeposition technology (LDT), laser repair technology (LRT), lasercladding technology (LCT), laser deposition welding (LDW), laserdeposition welding with integrated milling (LDWM), selective lasersintering (SLS), direct metal printing (DMP), and/or stereolithography(SLA) and/or any combination.

For example, the first housing portion 204, second housing portion 206,the valve body 1202, 1302, 1402, 1502, 1602, the disks 218, 1320, 1404,1508 and/or the flow control member 216, 1336, 1410, 1506 of theillustrated examples may be manufactured using an additive manufacturingprocess (e.g., direct metal laser sintering or 3D printing). In someexamples, the fluid apparatus 100 may be formed in an assembled statevia, for example, additive manufacturing. In some examples, the firsthousing portion 204, 1604, the second housing portion 206, 1606, and/orthe valve body 1202, 1302, 1402, 1502 may be formed via, for example,injection molding and the flow control member 216, 1336, 1410, 1506 maybe formed via additive manufacturing process(es), or vice versa. In someexamples, the flow control member 216, 1336, 1410, 1506 may be formedwith molten Teflonor Kel-F material via injection molding.

In some examples, some or all of the threads (e.g., the threads 406,734, 1608 the threads of the fittings 314 and 510, etc.) of the examplefluid apparatus 100, 1200, 1300, 1400, 1500 and/or 1600 disclosed herein(e.g., the first housing portion 204, 1604 second housing portion 206,1606, the valve body 1202, 1302, 1402, 1502, the disks 218, 1320, 1404,1508 and/or the flow control member 216, 1336, 1410, 1506) may be formedvia additive manufacturing process(es). In some examples, the threads406, 734, 1608 and/or the threads of the fluid apparatus 100, 1200,1300, 1400, 1500 and/or 1600 disclosed herein may be sized as2.000-12-UNC threading, or a range of course or fine threading sizes. Insome examples, the threads 406, 734, 1608 and/or the threads of thefluid apparatus 100, 1200, 1300, 1400, 1500 and/or 1600 may be powerscrews (e.g., a Joyce worm-gear screw jack). Example power screws areprovided by J. K. Nisbett and R. G. Budynas, Shigley's MechanicalEngineering Design, “The Mechanics of Power Screws”, chapter 8, section2, 9^(th) edition. In some examples, the threads (e.g., threads 406,734, 1608, the threads of the fittings 314 and 510) may be formed as asecondary process.

In some examples, after formation of the flow control member 216, 1336,1410, 1506, the disks 218, 1320, 1404, 1508, and/or the valve seats 220,1206, 1340, 1422, and 1504, the disks 218, 1320, 1404, 1508 and/or thevalve seats 220, 1206, 1340, 1422 and/or 1504 may be polished via asecondary process. For example, a lapping process may be employed on thefirst side 722 of the disks 218 and/or the valve seats 220, 1206, 1340,1422 and/or 1504 to allow for localized polishing to improve sealing(e.g., improve sealing classification). Additionally, in some examples,to reduce stress concentrations associated with cyclic loading orvibration, inner and/or outer surfaces of the example the example fluidapparatus 100, 1200, 1300, 1400, 1500 and/or 1600 disclosed herein mayinclude a radius of curvature or fillet (e.g., a 45 degree fillet) toreduce pointed or sharp edges and/or to provide smooth transitionsbetween differently dimensioned portions of the fluid apparatus. Forexample, inner and/or outer surfaces of the first housing portion 204,the second housing portion 206 (e.g., an inner surface of the secondhousing portion 206 and/or an outer surface of the second housingportion 206 (e.g., defining the stepped surfaces 610)), and/or the flowcontrol member 216 may include a radius of curvature or fillet (e.g., a45 degree fillet) to reduce pointed or sharp edges.

Additionally, the components of the example fluid apparatus 100, 1200,1300, 1400, 1500 and/or 1600 disclosed herein may be formed from thesame material or different material(s). For example, the first housingportion 204, 1604, second housing portion 206, 1606, the valve body1202, 1302, 1402, 1502, the disks 218, 1320, 1404, 1508 and/or the flowcontrol member 216, 1336, 141) 1506 of the illustrated examples may becomposed of Inconel 625, metal, aluminum, plastic,Polytetrafluoroehylene (PTFE), stainless steel, an alloy and/or anyother suitable material for use in, for example, propulsion systems,cryogenic applications, hydraulic systems, and/or any other material(s)or alloy. In some examples, the first housing portion 204, 1604, secondhousing portion 206, 1606, the valve body 1202, 1302, 1402, 1502 may beformed of a first material, the disks 218, 1320, 1404, 1508 may beformed of a second material, and/or the flow control member 216, 1336,1410, 1506 may be formed of a third material. In some examples, thefirst material is the same as the second material and/or the thirdmaterial. In some examples, the second material is the same as the thirdmaterial. In some examples, the first material is different from thesecond material and/or the third material. In some examples, the secondmaterial is different than the first material. In some examples, thedisks 218, 1320, 1404, 1508 are formed of different materials. In someexamples, the flow control member 216, 1336, 1410, 1506 may be formed(e.g., grown) with a Functionally Graded Materials process (e.g., an FGMprocess) such that a gradient of coefficient of thermal expansion (CTE)across the flow control member 216, 1336, 1410, 1506 provides varyingcracking-pressure gradients across the disks 218, 1320, 1404 (e.g.,across the three disks 710, 712, 714) with changes in temperatures,which may be useful for re-entry vehicles, passing multiple sonicregimes, or space vehicles that are periodically eclipsed from the sunby the earth. In sonic examples, the disks 218, 1320, 1404 may be formedwith material(s) having a coefficient of thermal expansion (e.g., Kel-F)that varies the cracking pressures of the disks 218 (e.g., the firstdisk 710, the second disk 712 and/or the third disk 714), 1320, 1404,based on a temperature to provide a continuum of cracking pressuresduring, for example, sonic and/or thermal regimes. For example,materials having a relatively high coefficient of thermal expansion maycause the cracking pressures of the disks 218, 1320, 1404 to vary basedon a temperature of a process fluid flowing through the fluid apparatus100 and/or a temperature of the environment surrounding the valveapparatus 100. In some examples, the disks 218, 1320, 1404 may becomposed of material(s) having a low coefficient of thermal expansionsuch that temperature of the process fluid and/or the environmentsurrounding the fluid apparatus 100 does not affect the crackingpressures of the disks 218, 1320, 1404. In this manner, the fluidapparatus disclosed herein may provide different performancecharacteristics during different portions of a flight mission. Forexample, the cracking pressures of the disks 218 may be a first crackingpressures during an ascent envelope of a mission and a second crackingpressure different than the first cracking pressure during a descentenvelope of a mission.

Additionally, the example flow control member 216, 1336, 1410, 1506disclosed herein may be a unitary piece or structure. However, in someexamples, the disks 218 or the disk 1508 may be formed separately fromthe pylon 702 of the flow control member 216 or 1506. In some examples,the disks 218 or the disk 1508 may be formed from a first materialdifferent from a material of the pylon 702. In some examples, the disks218 or the disk 1508 may be coupled or attached to the pylon 702. Forexample, the disks 218 or the disk 1508 may attach to the pylon viafasteners (e.g., mechanical fasteners, chemical fasteners), shrink fitand/or any other process(es). In some examples, the example fluidapparatus 1200, 1300, 1400, 1500 and/or 1600 disclosed herein (e.g., thefirst housing portion 204, 1604, second housing portion 206, 1606, thevalve body 1202, 1302, 1402, 1502, the disks 218, 1320, 1404, 1508and/or the flow control member 216, 1336, 1410, 1506) may be coated(e.g., sprayed) with an anti-tarnishing material(s) to prevent corrosionof the fluid apparatus 1200, 1300, 1400, 1500 and/or 1600 during non-useconditions.

Referring to FIG. 18, the method 1800 of the illustrated exampleincludes coupling the flow control member to the first housing portion(block 1802). For example, referring to FIG. 9, the example flow controlmember 216 is coupled to the first housing portion 204 or 1604 via thehead 704. A position of the flow control member is adjusted relative tothe first housing portion to provide a preload to the disks (block1804). For example, referring to FIG. 9, the head 704 of the flowcontrol member 216 is rotated about the longitudinal axis 214 to adesired position that provides a desired preload to the disks 218. Inparticular, the threads 734 of the head 704 engage the threads 406 ofthe first housing portion 204 to enable rectilinear adjustment of theflow control member 216 along the longitudinal axis 214. Once the head704 or the flow control member 216 is at a desired position, a fastener902 may be provided to maintain the position of the head 704 or the flowcontrol member 216 relative to the first housing portion 204.

The first housing portion is then coupled to the second housing portionto define a fluid flow passageway between an inlet and an outlet (block1806). For example, referring to FIG. 9, the first housing portion 204is coupled to the second housing portion 206 via the respective flanges308 and 504 and the fasteners 207. In some examples, the first housingportion 204 and the second housing portion 206 of FIGS. 1-6, 7A-7B,8A-8E, and 9-11, FIG. 15 and/or of FIG. 16 may be formed without theflanges 308 and 504. In some such examples, the first housing portion204, 1604 may be coupled to the second housing portion 206, 1606 viawelding (e.g., linear friction welding, heat welding, fusion), a clamp,rivets, threads, and/or any another fastener (e.g., mechanical fastener,a chemical fastener, etc.). Absent the flanges 308 and 504, the fluidapparatus 100, 1500 and 1600 may provide a relatively smaller footprint.For example, an outermost portion of an outer surface of the firsthousing portion 204, 1604 may be substantially flush with an outermostportion of an outer surface of the second housing portion 206, 1606 (toprovide a cylindrical profile). Referring to FIGS. 12-14, the portion ofthe method represented by block 1806 may be omitted when manufacturing,forming or assembling the example fluid apparatus 1200-1400.

Referring to FIG. 19, the method 1900 of the illustrated example beginsby receiving a fluid having a first pressure at an inlet of a valve(block 1902). For example, a fluid is received at the inlet 210 from theupstream source 102. The method 1900 includes enabling the fluid at theinlet to flow past a first disk positioned between the inlet and a firstchamber of a fluid flow passageway when the first pressure is greaterthan a first cracking pressure of the first disk (block 1904). Forexample, the fluid at the inlet 210 flows past the first disk 710 to thefirst chamber 1104. For example, when the fluid at the inlet 210 isgreater than a first cracking pressure of the first disk 710, theperipheral edge 718 of the first disk 710 deflects or moves away fromthe valve seat 604 to allow the fluid to flow to the first chamber 1104.For example, the first chamber 1104 is positioned between the inlet 210and the second disk 712. In the example shown in FIG. 15, the fluidflows to the outlet 212 after the first disk 710 moves to the openposition. In some examples, the fluid flows to the second chamber 1108when the first disk 710 moves to the open position.

In some examples, fluid in a first chamber is enabled to flow past asecond disk positioned between the first chamber and the second chamberof the fluid flow passageway when a second pressure of the fluid in thefirst chamber is greater than a second cracking pressure of the seconddisk (block 1906). For example, the fluid in the first chamber 1104flows past the second disk 712 and to the second chamber 1108 when thepressure of the fluid in the first chamber 1104 is greater than thesecond cracking pressure of the second disk 712. For example, when thepressure of the fluid in the first chamber 1104 is greater than thecracking pressure of the second disk 712, the peripheral edge 718 of thesecond disk 712 deflects or moves away from the second valve seat 606 toallow the fluid to flow to the second chamber 1108.

In some examples, the fluid in the second chamber is enabled to flow toan outlet of the fluid flow passageway when a pressure of the fluid inthe second chambers greater than a third cracking pressure of a thirddisk (block 1908). For example, the fluid in the second chamber 1108flows past the third disk 714 when the pressure of the fluid in thesecond chamber 1108 is greater than the third cracking pressure of thethird disk 714. For example, when the pressure of the fluid in thesecond chamber 1108 is greater than the cracking pressure of the thirddisk 714, the peripheral edge 718 of the third disk 714 deflects ormoves away from the third valve seat 608 to allow the fluid to flow tothe outlet 212.

In some examples, the first cracking pressure of the first disk 710, thesecond cracking pressure of the second disk 712 and/or the thirdcracking pressure of the third disk 714 is determined by the position ofthe flow control member 216 relative to the first housing 202 or thesecond housing 204. In some examples, the first cracking pressure isdifferent than the second cracking pressure and/or the second crackingpressure is different than the third cracking pressure. In someexamples, the first cracking pressure is equal to the second crackingpressure and/or the third cracking pressure.

In some examples, in operation, a vibrational force imparted to thedisks 218, 132, 1404, 1508 that is equal to a resonant frequency of thedisks 218, 132, 1404, 1508 may cause the disks 218, 132, 1404, 1508 toflake and cause debris to flow downstream. To ensure an aeroelastic,flutter-free design and/or to prevent or reduce flacking of the disks218, 132, 1404, 1508, the disks 218, 132, 1404, 1508 may be tested afterformation of the flow control member 216, 1336, 1410, 1506. For example,the fluid apparatus 100, 1200, 1300, 1400, 1500 and/or 1600 may betested with conditions or fluid characteristics that the fluid apparatus100, 1200, 1300, 1400, 1500 and/or 1600 may experience during operation.For example, during testing, the vibrational frequencies of the disks218, 132, 1404, 1508 may be measured or determined and compared to theresonant frequency of the respective disks 218, 132, 1404, 1508. If themeasured frequency is equal to the resonant frequency, a characteristicof the fluid apparatus 100, 1200, 1300, 1400, 1500 and/or 1600 such as,for example, the distances (e.g., vertical distances) between the disks218, 132, 1404, 1508 (e.g., distances D1, D2 and D3), the distances(e.g., vertical distances) between the valve seats 220, 1340, 1422, 1504(e.g., distances L2 and L2), the thicknesses of the disks 218, 132,1404, 1508, and/or the diameters of the disks 218, 132, 1404, 1508,etc., may be adjusted, altered, and/or modified (e.g., redesigned) toalter the resonant frequency of the disks 218, 132, 1404, 1508.

In some examples, a wall thickness of the example fluid apparatus 100,1200, 1300, 1400, 1500 and/or 1600 disclosed herein (e.g., the firsthousing portion 204, 1604 the second housing portion 206, 1606 and/orthe valve body 1202, 1302, 1402, 1502) may be configured (e.g.,dimensionally sized) using the following Modified-Goodman Equations 1-6:

$\begin{matrix}{{\frac{\sigma_{a}}{S_{e}} + \frac{\sigma_{m}}{S_{y}}} = \frac{1}{n}} & {{Eq}.\mspace{14mu} 1} \\{\sigma_{a} = \frac{Pd}{2t}} & {{Eq}.\mspace{11mu} 2} \\{n = {2\left( {{safety}\mspace{14mu} {factor}} \right)}} & {{Eq}.\mspace{14mu} 3} \\{\sigma_{m} = {\sigma_{a}/2}} & {{Eq}.\mspace{14mu} 4} \\{{\frac{\sigma_{a}}{2}\left( {\frac{1}{S_{e}} + \frac{1}{S_{y}}} \right)} = \frac{1}{n}} & {{Eq}.\mspace{14mu} 5} \\{t = {{n(P)}\left( \frac{d}{4} \right){\left( {\frac{1}{S_{e}} + \frac{1}{S_{y}}} \right).}}} & {{Eq}.\mspace{14mu} 6}\end{matrix}$

where: σ_(a) is amplitude stress; S_(e) is endurance limit from MarinEquation; σ_(m) is midrange stress; S_(y) is yield strength; n is factorof safety; S′_(e) is test speciment endurance limit;

-   S_(ut) is ultima strength; where the k_(a)-k_(f) values are obtained    from marine K value equations:-   k_(a) is surface condition modification factor; k_(b) is size    factor; k_(c) is loading factor;-   k_(d) is temperature factor; k_(e) is reliability factor; k_(f) is    miscellaneous—effects factor;-   and t is thickness.

For example, a wall thickness of the first housing portion 204 and/orthe second housing portion 206 of FIGS. 1-11, made from material Inconel625, configured to have a maximum pressure rating of 100 psi, provides athickness of 0.2075 inches as follows:

$\begin{matrix}{S_{y} = {40 \times 10^{3}{psi}}} & {{Eq}.\mspace{14mu} 7} \\{S_{e}^{\prime} = {20 \times 10^{3}{psi}}} & {{Eq}.\mspace{14mu} 8} \\{S_{ut} = {100 \times 10^{3}{psi}}} & {{Eq}.\mspace{14mu} 9} \\{k_{a} = {{a\left( S_{ut} \right)}^{b} = {{2.7\left( {100 \times 10^{3}} \right)^{- 0.265}} = 0.128}}} & {{Eq}.\mspace{14mu} 10} \\{k_{b} = {{0.91d^{- {.157}}} = 0.732}} & {{Eq}.\mspace{14mu} 11} \\{k_{c} = {0.85({axial})}} & {{Eq}.\mspace{14mu} 12} \\{k_{d} = {1({cryo})}} & {{Eq}.\mspace{14mu} 13} \\{k_{e} = {{0.620@99.9999}\% \mspace{14mu} {Reliability}}} & {{Eq}.\mspace{14mu} 14} \\{k_{f} = 1} & {{Eq}.\mspace{14mu} 15} \\{S_{e} = {{S_{e}^{\prime}\left( k_{a} \right)}\left( k_{b} \right)\left( k_{c} \right)\left( k_{d} \right)\left( k_{e} \right)\left( k_{f} \right)}} & {{Eq}.\mspace{14mu} 16} \\{{S_{e} = {{\left( {20 \times 10^{3}} \right)(0.128)(0.732)(0.85)(1)(0.620)(1)} = 987.56}}{t = {{2(100)\left( \frac{4}{4} \right)\left( {\frac{1}{987.56} + \frac{1}{40 \times 1^{3}}} \right)} = {0.2075\mspace{14mu} {inches}}}}} & \;\end{matrix}$

In some examples, the wall thickness of the example fluid apparatus 100,1200, 1300, 1400, 1500 and/or 1600 disclosed herein (e.g., the firsthousing 204, 1604 and/or the second housing 206, 1604) may be determinedusing Finite Element Analysis doublet-lattice solver. In some examples,the wall thickness of the example fluid apparatus 100, 1200, 1300, 1400,1500 and/or 1600 disclosed herein (e.g., the first housing and/or secondhousing) may be verified using the following wall-thickness equation:

$\begin{matrix}{{\sigma_{a} = \frac{{P_{i}R_{i}^{2}} - {P_{0}R_{0}^{2}} - \frac{R_{i}^{2}{R_{0}^{2}\left( {P_{0} - P_{i}} \right)}}{R^{2}}}{R_{0}^{2} - R_{j}^{2}}};} & {{Eq}.\mspace{11mu} 17}\end{matrix}$

where, σ_(a) is largest at R=R_(i): P_(i) is an inner pressure; P_(o) isan outer pressure; R_(i) is an inner radius (i.e., the radius betweenthe longitudinal axis and the inner surface of the first housing or thesecond housing), R_(o) is an outer radius (i.e., the radius between thelongitudinal axis and the outer surface of the first housing or thesecond housing); and R is the location to determine stress.

The fasteners 207 may be tightened in a star pattern to facilitate aseal between the flanges 308 and 504 (e.g., evenly distribute loadacross a circumference of the seals). In some examples, the fasteners207 may be pre-loaded with a specific torque. In some examples, safetywires, lock-nuts, Loctite® and/or any other fastener may be employed toensure pre-loading in the presence of vibration. In some examples, bolttorque pre-loading of the fasteners 207 may be determined with thefollowing equations:

T=K*F _(i) *d   Eq. 18:

K=0.2   Eq. 19:

F _(i)=0.75*F _(p)   Eq. 20:

F _(p) =A _(t) *S _(p)   Eq. 21:

S _(p)=0.85*S _(y)   Eq. 22:

where, T is torque; F_(i) is preload; K=torque coefficient; d is majordiameter; F_(p) is proof load; S_(p) is proof strength, A_(t) istensile-stress area; and S_(y) is yield strength. For example, a majordiameter of 0.25 inches, a tensile-stress area of 0.0318, a yieldstrength of 92 kpsi, a proof strength of 0.85(92 kpsi), and a torquecoefficient of 0.2 would require a torque of 7.77 ft-lb.

A_t=0.0318

S_y=92 kpsi

F _(—p)=(0.0318(0.85)(92*10̂3)

F_i=(0.75)(0.0318)(0.85)(92*10̂3)

T=(0.2)(0.75)(0.0318)(0.5)(92*10̂3)(0.25)(1/12)

T=7.77 ft-lb

Disk deflection of the disks 218, 1320, 1404 and/or 1508 may bedetermined via Roark's equations. For example, deflection of a diskhaving an outer free edge and an inner fixed edge may be determined fromthe flowing equations:

$\begin{matrix}{M_{rb} = {\frac{- {qa}^{2}}{C_{8}}\left\lbrack {{\frac{C_{9}}{2\; {ab}}\left( {a^{2} - r_{0}^{2}} \right)} - L_{17}} \right\rbrack}} & {{Eq}.\mspace{14mu} 23} \\{Q_{b} = {\frac{q}{2\; b}\left( {a^{2}r_{0}^{2}} \right)}} & {{Eq}.\mspace{14mu} 24} \\{y_{a} = {{M_{rb}\frac{a^{2}}{D}C_{2}} + {Q_{b}\frac{a^{3}}{D}C_{3}} - {\frac{{qa}^{4}}{D}L_{11}}}} & {{Eq}.\mspace{14mu} 25} \\{\theta_{a} = {{M_{rb}\frac{a}{D}C_{5}} + {Q_{b}\frac{a^{2}}{D}C_{6}} - {\frac{{qa}^{3}}{D}L_{14}}}} & {{Eq}.\mspace{14mu} 26} \\{C_{2} = {\frac{1}{4}\left\lbrack {1 - {\left( \frac{b}{a} \right)^{2}\left( {1 + {2\; \ln \frac{a}{b}}} \right)}} \right\rbrack}} & {{Eq}.\mspace{14mu} 27} \\{C_{3} = {\frac{b}{4a}\left\{ {{\left\lbrack {\left( \frac{b}{a} \right)^{2} + 1} \right\rbrack \ln \frac{a}{b}} + \left( \frac{b}{a} \right)^{2} - 1} \right\}}} & {{Eq}.\mspace{14mu} 28} \\{C_{8} = {\frac{1}{2}\left\lbrack {1 + v + {\left( {1 - v} \right)\left( \frac{b}{a} \right)^{2}}} \right\rbrack}} & {{Eq}.\mspace{14mu} 29} \\{C_{9} = {\frac{b}{a}\left\{ {{\frac{1 + v}{2}\ln \frac{a}{b}} + {\frac{1 - v}{4}\left\lbrack {1 - \left( \frac{b}{a} \right)^{2}} \right\rbrack}} \right\}}} & {{Eq}.\mspace{14mu} 30} \\{L_{11} = {\frac{1}{64}\left\{ {1 + {4\left( \frac{r_{0}}{a} \right)^{2}} - {5\left( \frac{r_{0}}{a} \right)^{4}} - {4{\left( \frac{r_{0}}{a} \right)^{2}\left\lbrack {2 + \left( \frac{r_{0}}{a} \right)^{2}} \right\rbrack}\ln \frac{a}{r_{0}}}} \right\}}} & {{Eq}.\mspace{14mu} 31} \\{L_{17} = {\frac{1}{4}\left\{ {1 - {\frac{1 - v}{4}\left\lbrack {1 - \left( \frac{r_{0}}{a} \right)^{4}} \right\rbrack} - {\left( \frac{r_{0}}{a} \right)^{2}\left\lbrack {1 + {\left( {1 + v} \right)\ln \frac{a}{r_{0}}}} \right\rbrack}} \right\}}} & {{Eq}.\mspace{14mu} 32}\end{matrix}$

where;

y_(b)=0

θ_(b)=0

M_(ra)=0

Q_(a)=0

and, where the K values are provided from table 1.

TABLE 1 b/a 0.1 0.3 0.5 0.7 0.9 K_(ya) −0.0757 −0.0318 −0.0086 −0.0011K_(θa) −0.0868 −0.0512 −0.0207 −0.0046 −0.00017 K_(Mrb) −0.9646 −0.4103−0.1736 −0.0541 −0.00530

Stress-strain relationship of the disks 218, 1320, 1404 and/or 1508 maybe determined via Roark's equations. For example, stress or strain of adisk having an outer free edge and an inner fixed edge may be determinedfrom the flowing equations:

$\begin{matrix}{\sigma = \frac{6\; M}{t^{2}}} & {{Eq}.\mspace{11mu} 33}\end{matrix}$

where σ is stress, M is moment, and t is disk thickness. Equation 33,for example, can be used to determine maximum stress on the disks 218,1320, 1404 and/or 1508 where the disks attach to the pylon 702. Theplate constant D can be obtained from the following equation:

$\begin{matrix}{{D = \frac{{Et}^{2}}{12\left( {1 - v^{2}} \right)}};} & {{Eq}.\mspace{11mu} 34}\end{matrix}$

where D is the plate constant, E is the modulus of elasticity, t is thedisk thickness, and v is Poisson's ratio.

Although certain example apparatus and methods have been describedherein, the scope of coverage of this patent is not limited thereto. Onthe contrary, this patent covers all methods, apparatus and articles ofmanufacture fairly falling within the scope of the amended claims eitherliterally or under doctrine of equivalents.

What is claimed is:
 1. A fluid apparatus comprising: a valve bodydefining a fluid flow passageway and a plurality of valve seats; and aflow control member positioned in the fluid flow passageway of the valvebody, the flow control member having a plurality of disks, a respectiveone of the disks to move relative to a respective one of the valve seatsto control fluid flow through the valve body, the flow control memberbeing adjustable relative to a longitudinal axis of the valve body toprovide a preload to the disks, each of the disks has a crackingpressure corresponding to the preload.
 2. The apparatus of claim 1,further including a bonnet to couple to the valve body after the flowcontrol member is positioned in the fluid flow passageway.
 3. Theapparatus of claim 1, wherein the valve body includes an inner surfacedefining a threaded wall adjacent the valve seats.
 4. The apparatus ofclaim 3, wherein the flow control member includes a threaded portion toengage the threaded wall of the valve body to enable adjustment of theflow control member relative to the longitudinal axis.
 5. The apparatusof claim 1, wherein the flow control member includes a tool receivinginterface to enable rotation of the flow control member relative to thevalve body.
 6. The apparatus of claim 5, wherein the tool receivinginterface includes a gear.
 7. The apparatus of claim 1, furtherincluding a plurality of pillars radially spaced relative to thelongitudinal axis and positioned between the disks, the pillars to causethe disks to move simultaneously between an open position and a closedposition when a first disk of the plurality of disks moves between theopen position and the closed position.
 8. The apparatus of claim 1,wherein the valve body includes an inner surface having a plurality ofstepped surfaces to define the plurality of valve seats.
 9. An apparatuscomprising: a valve body defining a valve seat positioned in a fluidflow passageway between an inlet and an outlet and a threaded innerwall; and a flow control member positionable in the fluid flowpassageway, the flow control member including: a body; a disk coupled tothe body, the disk to seal against the valve seat to prevent fluid flowthrough the fluid flow passageway when a pressure at an inlet of thevalve body is less than a cracking pressure of the disk, and the disk tomove away from the valve seat to allow fluid flow through the fluid flowpassageway when the pressure at the inlet of the housing is greater thanor equal to the cracking pressure; and a head having threaded portion toengage the threaded inner wall of the valve body to couple the flowcontrol member to the valve body, the head being adjustable relative toa longitudinal axis of the valve body to provide a preload to the diskcorresponding to the cracking pressure.
 10. The apparatus of claim 9,further including a bonnet to couple to the valve body, the bonnethaving a cavity defining an outlet of the fluid flow passageway.
 11. Theapparatus of claim 9, wherein the head has an annular wall spaced fromthe body, the annular wall being attached to the body via a plurality ofribs, an outer surface of the annular wall having the threaded portion.12. The apparatus of claim 9, wherein the head includes a plurality ofpassageways to allow fluid flow between a first side of the headoriented toward the inlet and a second side of the head orientedopposite the inlet.
 13. The apparatus of claim 9, wherein the valve seatof the valve body includes a plurality of valve seats spaced along thelongitudinal axis of the valve body.
 14. The apparatus of claim 13,further comprising a plurality of disks, each of the disks to moverelative to a respective one of the valve seats to control fluid flowthrough the valve body.
 15. The apparatus of claim 9, wherein the diskincludes a center portion coupled to the body and a peripheral edgeextending from the center portion to engage the valve seat, theperipheral edge of the disk to move relative to the valve seat tocontrol fluid flow through the fluid flow passageway.
 16. A methodcomprising: positioning a flow control member in a first housing of afluid valve, the first housing having a plurality of valve seats and theflow control member having a plurality of disks, the valve seats and thedisks being spaced along a longitudinal axis of the first housing, arespective one of the disks is to engage a respective one of the valveseats when the flow control member is positioned in the first housing;and adjusting a position of the flow control member relative to thelongitudinal axis to vary a preload of the plurality of disks.
 17. Themethod of claim 16, further including coupling a second housing to thefirst housing after adjusting the position of the flow control member,the first housing and the second housing to define a fluid flowpassageway between an inlet and an outlet of the fluid valve.
 18. Themethod of claim 16, wherein the adjusting the position of the flowcontrol member includes rotating the flow control member about thelongitudinal axis.
 19. The method of claim 18, wherein adjusting theposition of the flow control member includes threadably coupling a headof the flow control member to an inner surface of the first housing. 20.The method of claim 19, further including providing a fastener adjacentthreads of the head and threads of the inner surface of the firsthousing to secure a position of the flow control member along thelongitudinal axis.